JPH0577730A - Steering truck for rolling stock car - Google Patents

Abstract

PURPOSE:To eliminate unneeded steering functions to ensure a stabilized travel in a struck in which the position of an axle box is displaced in response to oscillating displacement between a car body and the truck by providing arm mechanisms for subtracting the right and left longitudinal displacements between the truck and the car body to detect only the amount of oscillation of the truck. CONSTITUTION:When a tractive force acts on trucks and a longitudinal displacement occurs between the trucks, displacement detecting links 15A, 15B are, for example, pressed to the right side to rotate clockwise to pull upper connecting links 19A, 19B to the right side. At the same time, lower detecting arms 17A, 17B press lower connecting arms 20A, 20B to the left side. Thus, truck-rotational angle detecting arms 12A, 12B are rotated clockwise, but steering command links 11A, 11B are fixed in the right and left direction not to act. On the other hand, when a car body comes into a curved track, and the center of the car body comes to the left side of a truck linkage mechanism, the steering command link 11A moves to the right side, the steering command link 11B moves to the left side, and the truck is steered through steering arms 6A, 6B and steering links 4A-4D.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a forced steering bogie of a bolsterless bogie in which a bolster is not provided between the bogies of a railway vehicle.

[0002]

2. Description of the Related Art There are various methods for railway vehicle steering bogies. One of them is to detect the swing angle of the bogie with respect to the vehicle body to estimate the running curve radius and to extend the extension line of the axle at the center point of the curve. There is a method to control the position of the axle box so that

Generally, a spring mechanism is provided in the front-rear direction between the bogie and the vehicle body to deal with vibration of the bogie, especially when the vehicle body is rocked back and forth during pitching. When power is applied, the carriage is displaced from the vehicle body by a certain amount.

Such a phenomenon has an effect that the pitching of the bogie causes the fluctuation of the tractive force in a locomotive or the like in which the tractive force transmission point between the vehicle body and the bogie is made as low as possible and the axle load movement is prevented. Therefore, a much larger displacement than that of a train or the like is allowed between the bogie and the vehicle body in the front-rear direction.

[0005]

As described above, the traction force,
In the case of a locomotive bogie where the space between the car body and the bogie tends to move back and forth due to fluctuations in the braking force, the bogie swing angle is a combination of the simple back and forth motion between the car body and the front and rear motion that requires steering. Occurs. However, it is difficult for the above-mentioned conventional steering cart mechanism to detect the swinging angle, so it is difficult to exert the steering function, and it is necessary to separate the swinging angle of the truck individually and apply it to the steering mechanism. Become. SUMMARY OF THE INVENTION It is an object of the present invention to configure a steering cart having a shock absorbing mechanism in the front-rear direction between a vehicle body and a truck as a forced steering mechanism.

[0006]

A link mechanism for detecting a longitudinal displacement between a vehicle body and a dolly is arranged on the left and right sides of the dolly, and there is a point that the left and right link mechanisms do not move when they move in the same direction by the same amount. A link mechanism is provided so that the steering mechanism operates when the links move in different directions.

[0007]

With the above structure, the simple displacement in the front-rear direction between the vehicle body and the bogie and the simple displacement in the swinging direction can be decomposed and detected, so that the bogie steering can be operated only by the displacement in the swinging direction. become. Then, when longitudinal movement is transmitted to the vehicle body due to pitching of the truck, or when a large traction force is exerted, or when some impact force acts on the vehicle body and a traction force that exceeds the maximum adhesive force occurs, Since it can take a large buffering force, it will be absorbed.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A steering mechanism according to the present invention will be described based on an embodiment shown in FIGS. The steering link mechanism provided on the truck will be described. Front and rear wheels 1A-1D, its axles 2A, 2B
Two sets of wheel sets are configured by the above, and the axle boxes 3A to 3D are arranged on the wheel sets to receive the vehicle body load, driven by the electric motor, and controlled by the braking device.

Steering links 4A to 4D are attached to the axle boxes 3A to 3B, respectively, and the other ends of the steering links 4A to 4D are fixed to a steering arm fixing pin 5.
The steering arms 6A and 6B are alternately connected to each other around A and 5B.

One end of each of the front and rear links 7A and 7B is a steering arm.
Connect to the lower ends of 6A and 6B, and connect the other end to triangular links 8A and 8B. The left and right triangular arms 8A, 8B are connected by a left-right link 9, and fixed rotatably by fixing pins 10A, 10B. Attach the steering command links 11A, 11B to the tips of the steering arms 6A, 6B,
The other end is connected to the cart rotation angle detection arms 12A and 12B.

Underbody floor bracket attached to the underside of the vehicle body floor
Displacement detection links 15A, 15B are connected between 13A, 13B and the tip of the vehicle body displacement detection arms 14A, 14B. The body bogie displacement detection arm 14A is connected to the lower detection arm 17B on the opposite side by a displacement detection bar 16A, and similarly the body bogie displacement detection arm 14B is connected.
Is also connected to the lower detection arm 17A on the opposite side by the displacement detection bar 16B. The displacement detection bars 16A, 17B are supported by displacement detection bar receivers 18A, 18B fixed to the bogie frame. Displacement detection bar 16A, 16B
Connecting link 18A, 18B on top of the vehicle body displacement detection arm 14A, 14B at a certain distance above the connecting point
Like the upper connecting links 19A and 19B, the lower connecting links 20A and 20B are attached to the lower ends of the lower detecting arms 17A and 17B at a certain distance downward, and the upper connecting links are attached to the upper ends of the carriage rotation angle detecting arms 12A and 12B. 19A and 19B are connected at their tips, and the lower connecting links 20A and 20B are the cart rotation angle detection arms 12A and 12B.
It is connected to the lower end of the steering wheel mechanism.

The vehicle body 21 is mounted on a carriage 23 via a pillow spring 22, and the carriage 23 has an axial spring pot (not shown). Inside the axial spring pot, axial springs 24A and 24BV are provided, and the vehicle body weight is Axis box
It is related to 3A and 3C. A cushioning rubber device 26A, 26B is provided on the bottom surface of the vehicle body 21 and at the lower end of the vehicle body legs 25A, 25B hanging in a diagonal position of the carriage.
The shock-absorbing rubber device 26 by tilting the push rods 27A and 27B.
Connect to A and 26B. The center line extension of the inclined push rods 27A and 27B should intersect at the center of the carriage 23 near the rail surface. Push rod
The traction links 28A and 28B connected to 27A and 27B are connected to each other in a Z shape in the carriage 23 to form a shaft load movement preventing link mechanism. The operation of the present invention having the above configuration will be described.

When a traction force acts on the carriage 23, the push rods 27A and 27B
It acts on the vehicle body feet 25A, 25B via the cushioning rubber devices 26A, 26B. At this point, the cushioning effect of the cushioning rubber devices 26A and 26B
A back and forth movement of the order of 10 mm occurs in the carriage 23.

In the axle load movement preventing bogie, the link mechanism of the traction device is characterized by the fact that the bogie and the vehicle body pitch each other around the position of the rail surface at the center of the bogie as the axle weight movement preventing bogie. On the other hand, in the case of bogies for electric trains, when the bogies are pitched, the height of the bolster anchor that connects the bogies to the vehicle body is placed at approximately the center of the axle box so that the bogie pitching does not cause longitudinal displacement. The longitudinal displacement on the floor of the vehicle and the upper part of the bogie is reduced. However, since the front-rear cushioning mechanism is provided between the bogie bodies, the front-rear displacement occurs even if there is a difference in the amount of movement.

Explaining the case where a longitudinal displacement occurs between the bogies, when the displacement detecting links 15A, 15B are pushed to the right by the longitudinal displacement, the displacement detecting links 15A, 15B move around the displacement detecting bars 16A, 16B. Rotate clockwise and pull the upper connecting links 19A, 19B to the right. On the other hand, since the displacement detection bars 16A and 16B simultaneously rotate clockwise, the lower detection arms 117A and 17B protruding downward from the displacement detection bars 16A and 16B push the lower connecting arms 20A and 20B to the left. become. By the above, the cart rotation angle detection arm 12Aa, 12B
Rotates clockwise, and the steering command links 11A and 11B connected to the center are fixed in the left-right direction and do not act. Therefore, a simple forward / backward movement between the bogies does not affect the steering link mechanism.

Next, as an example, a case where the body center is on the left side of the bogie link mechanism and the center of R from the wheels 1A and 1B moves to the right to enter the front side track is a bird's eye view. When the carriage 23 gradually swings in the clockwise direction and advances, the displacement detection link 15A is pushed and the displacement detection link 15B is pulled. Due to the displacement, the body carriage displacement detection arm 14A rotates clockwise around the displacement detection bar 16A, and the body carriage displacement detection arm 14B on the opposite side rotates counterclockwise around the displacement detection bar 16B and the lower connecting link. 19A moves to the right and upper connecting link 20B moves to the left. Next, the upper connecting link 20B moves to the left and the lower connecting link 20A moves to the right. With the above movement, the cart rotation angle detection arm
12A moves in parallel to the right and 12B moves in parallel to the left. The movement of the trolley rotation angle detection arms 12A and 12B causes the steering command link 11A to move to the right, and the steering arm 6A
Rotates clockwise, the steering links 4A, 4C are drawn toward the center of the bogie, and the gap between the axle boxes 3A, 3C becomes smaller. Next, the steering command link 11B moves to the left, the operation rudder arm 6B rotates counterclockwise, and the steering links 4B and 4D are extruded toward the outside of the carriage 23, and the gap between the axle boxes 3B and 3D becomes large. By the above operation, the gap between the axle boxes 3A and 3C is reduced and the gap between the axle boxes 3B and 3D is increased, so that the center lines of the axles 3A and 3B intersect on the front side of the carriage 23 and the carriage is centered on the intersection point. 23 starts to make a turning motion. Therefore, if the intersection point coincides with the R center point of the track curve, the steering function will be fully exerted when the diameter of the left and right wheels is proportional to the distance from the center of the curve due to the taper of the wheel tread. The conditions for the steering function to fully operate when the vehicle enters a curved road and the carriage 23 shakes its head will be described with reference to FIG. Here, R ... Curve radius L ... Distance between bogie core discs 1 ... Bogie shaft distance Θ ₁ … Angle between curve center and body center and bogie center Θ ₂ … Angle from curve center to bogie center and wheel axle center A = Y ... Bogie swing detection amount B ... Axle box clearance C ... Distance to left and right bogie displacement detection arms

With the vehicle body 21 of L riding on the curve of R and the carriage 23 swinging its neck in the direction of the curve, the wheels 1A to
When 1D is steered and the center line extensions of the axles 2A and 2B intersect at the center point O of the curve R, the carriage 23 is ideally steered. For this reason, the axle boxes 3A to 3D measure the amount of movement inside the carriage 23, and the amount of swing of the carriage detected by the body displacement detection arms 14A and 14B according to the swing angles of the body 21 and the carriage 23 will be examined.
First, the required displacement of the axle boxes 3A to 3D in the bogie frame is X = Θ ₂ × B / 2 …………………… (1) where Θ ₂ is expressed as follows. .. Θ ₂ = l / 2R ………………………… (2) From equations (1) and (2), the required movement X of the axle box is X = (l / 2R) × B / 2 = lB / 4R …… (3) Next, the body bogie displacement detection arms 14A and 14 by swinging the bogie.
The bogie swing amount Y detected at B is Y = Θ ₁ × C / 2 …………………… (4) where Θ ₁ is shown as follows Θ ₁ = L / 2R …… ………………………… (5) (4) From formula (5), the bogie swing detection amount Y is Y = (L / 2R) × C / 2 = LC / 4R …… (6) where Y The ratio of the required movement amount X of the shaft box to the detection amount is X / Y = (lB / 4R) / (LC / 4R) = lB / LC (7) Next, Fig. 4 shows the length of the levers of links. of a is shown by l ₁ to l _4, overall lever ratio M of the lever is _{M = (l 2 / l 1} ) × l 4 / l 3 = l 2 l 4 / l 1 l 3 ......... ( 8) If this is equal to Eq. (7), this trolley will be able to steer ideally. X / Y = M = l B / LC = l ₂ l ₄ / l ₁ l ₃ (9) Therefore, if the formula (9) is satisfied, no matter what the radius of the curve,
The steering cart of the present invention enables ideal steering.

As described above, the steering mechanism of the present invention separates the movement between the carriage 23 and the vehicle body 21 into longitudinal displacement and swing displacement.
Since the bogie steering function acts only on the swing displacement,
It is possible to prevent abnormal vibration from occurring in the vehicle due to abnormal steering performed while the vehicle is traveling under various conditions. As another embodiment of the present invention, a rod mechanism shown in FIG. 5 will be described.

If it is attempted to forcibly perform the displacement of the axle box by using the detected displacement generated in the steering link mechanism, the wheels 3A ...
It may be necessary to force the 3D to slide, and there is a risk of excessive force. In this case, this rod mechanism may be used as a mechanism for transmitting only the force to release the displacement. This rod mechanism applies the initial compression to the spring 29 and
A seat plate 32 and a collar 33 are assembled in a spring housing 31 of 30.

When a force is transmitted by the seat plate 32 and the collar 33, the spring
Up to the initial compression force of 29, the front and rear rods 30,34 operate without displacement, but if an abnormal force acts on the initial compression force, the force is transmitted by the initial compression force and the spring force, and the tensile force and the pushing force are It is possible to prevent the rod length from displacing even if it acts and transmitting an excessive acting force. This rod mechanism is equipped with displacement detection links 15A and 15B.
Alternatively, it can be incorporated into the steering command links 11A and 11B.

[0021]

With the mechanism of the present invention, the bogie steering is carried out by detecting only the swinging angle component of the bogie with respect to various movement displacements between the bogies of the vehicle body, so that an unnecessary steering function does not act. As a dolly, stable running is possible.

[Brief description of drawings]

FIG. 1 is a perspective view of a bogie steering mechanism according to the present invention.

FIG. 2 is a side view of a truck according to the present invention.

FIG. 3 is an explanatory diagram of a steering action of a steering cart.

FIG. 4 is an explanatory diagram of a steering link mechanism of a truck.

FIG. 5 is a sectional view of a rod structure of another embodiment.

[Explanation of symbols]

 2 axles 3 axle box 4 steering link 6 steering arm 11A, B steering command link 12A, B carriage rotation angle detection arm 14A, B body carriage displacement detection arm 15A, B displacement detection link 17A, B lower detection arm 19A, B upper connection Link 20A, B Lower connection link 21 Body 23 Truck

Claims (1)

[Claims] 1. A steering trolley for displacing an axle box position in accordance with a swing displacement between body trolleys to direct an extension of a center line of an axle to a center point of a vehicle traveling curve. A steering bogie for a railway vehicle, which is characterized by a steering device with an arm mechanism that detects only the amount of swinging of the bogie by subtracting the longitudinal displacements of each.